Centrifugal pump



Aug. 29, 1961 K. J. HEINIKE CENTRIFUGAL PUMP 2 Sheets-Sheet 2 Filed June 13, 1960 FI G. 5

Fl 6. 7 INVENTOR.

Kurt J. Henicke BY %VM%L^ Attorney E: l G. 8

United States Patent() 2,997,958 CENTRIFUGAL PUMP Kurt J. Heinicke, Hollywood, Fla., assignor to Heinicke Pump Co., Hollywood, Fla., a corporation of Florida Filed June 13, 1960, Ser. No. 35,624 8 Claims. (Cl. 1033-193) This invention relates to improvements in pumps and has particular reference to centrifugal or similar pumps for the pumping and distribution of various uids. V

The prime purpose of this invention yresides in forming a pump of centrifugal or other character, primarily of of the pumps and the external surface of the impeller, is

practically impossible with respect to the inner surfaces and vanes of the impeller, resulting in a lowered efciency of the pump, due largely to turbulence of the iiuid and friction caused by the normally rough casting of the impeller.

The pump of the present invention as formed substantially of polished sheet metal stampings, welded and connected in a novel manner, results in a pump that is much lighter in weight than conventional cast pumps, cheaper to manufacture and is approximately 25% more eicient in operation,

The pump of the present invention comprises a connector housing that is bolted to the end portion ofa prime mover, a seal plate for the housing and a'bell housing for the impeller and with each of the units being circumferentially hanged and connected together by a novel type of clamping and sealing ring whereby the chamber of the bell housing, dened by the bell housing and the seal plate are rigidly clamped together in concentric relation and sealed with respect to the connector.

The invention further contemplates novel seal devices between the impeller and the seal plate whereby to'prevent the leakage of fluid from the bell housing to the area between the connector and the seal plate under the inuence of pressure generated by the impeller.

The invention further contemplates seal means between the impeller and the seal plate that is formed of noncorrosive materials and with a pressure exerting member being formed of a non-metallic yieldable member that imparts a constant sealing pressure with respect to a seal member disposed within the seal plate.

Novel features of construction, assembly and operation of the device will be more clearly apparent during the course of the following description, reference being had to the accompanying drawings wherein has been illustrated a preferred embodiment of the device and wherein like characters of reference are employed to denote like parts throughout the several iigures.

In the drawings:

FIGURE `1 is a side elevational view of a pump constructed in accordance with the invention,

FIGURE 2 is a front elevational view thereof,

FIGURE 3 is an enlarged central vertical sectional view taken substantially on line 3--3 of FIGURE 2,

FIGURE 4 is a fragmentary sectional view illustrating a novel form of clamp and sealing means between the several housing units of the pump, taken on 4-4 of FIGURE l,

FIGURE 5 is a sectional view taken substantially on line 5-5 of FIGURE 3,

"ice

FIGURE 6 is a sectional view taken substantially on line 6-6 of FIGURE 3,

FIGURE 7 is a sectional view taken substantially on line 7-7 of FIGURE 3, and

FIGURE 8 is an enlarged sectional view of a nonmetallic yieldable sealing unit.

Referring specifically to the drawings, the numeral 10 designates a prime mover, here illustrated as an electric motor having a forward face 11 and an extending drive shaft 12.

The pump comprises essentially an open cylindrical connector 13, a seal plate 14, a bell housing 15 and an impeller .16, all stamped or otherwise formed of aA relatively highly polished sheet metal, such as steel, brass, bronze, copper, stainless steel, Monel, aluminum, titanium, etc. f

The connector 13 embodies a band 17 of predetermined width having inwardly directed circumferential flange l18 that is at a right angle to the band. The opening dened by the flange 18 may vary in accordance with the particular type of motor employed and here has been proportioned to engage overa raised end portion of the motor casing. The flange `18 is apertured at equidistantly spaced points for the passage of fastening devices 19 through the medium of which the connector is rigidly connected to the end ofthe motor concentric thereto. The band 17 is provided with an outwardly ydirected and relatively short circumferential `flange 20, for a purpose to be presently described.

The seal plate 14 embodies a non-at plate 21 having a forwardly extending circumferential flange 22 that has a diameter to snugly engage into the band 17. The flange 22 terminates in a right angle ange 23 that is concentric to the ange 20 and of slightly less diameter. 'I'he plate 21 has been stamped to provide a rearwardly extending socket 24 for the seating reception of a seal ring 25, formed of plastics or similar material. The socket 24 is centrally disposed with respect to the plate 21 and at assembly, is concentric to the shaft 12. The ring 25 supports a non-metallic bearing seal ring 26, formed of any suitable material, such as a ceramic or polished glass. The ring 25 and the bearing ring 26 are Idisposed in concentric relation to the shaft i12 and in spaced relation thereto.

The bell housing 15 is of a predetermined depth and has been shaped to accommodate the rotary impeller 16, the housing 15 is circumferentially anged, as at 27 `and with the flange being concentric to4 and of an identical diameter to the flange 20. The flanges 20, 23 and 27 at assembly of the pump are adapted to be held in concentric contacting engagement by a circumferential clamping band 28. The band 28 is U-shaped in cross section for receiving a non-metallic compressble clamping ring 29, preferably formed of rubber or nylon. The free ends of the ring 28 are provided with tubular sockets 30, receiving a threaded clamping screw 31 whereby the ring is compressed against the ilanges 20, 23 and 27 and with the ring 29 being distorted to seat within a circumferential groove formed by the shorter flange 23. The clamping yring 28 constitutes the connecting and sealing means between the several units formed by the connector 13, the seal plate 14 `and the bell housing 15 and successfully seals the several flanges in connected engagement against the escape of pressurized iluid within the chamber 15 formed by the bell housing and the seal plate 14.

The bell housing 15 is of a predetermined depth and has been shaped to accommodate the rotary impeller 16. The end wall 32 of the housing 15 is centrally apertured at 33 and with the aperture being in axial alignment with the motor shaft 12. An externally projecting coupling 34 is welded or otherwise lixedly connected into the aper ture 33 and serves as the connecting means for the fluid 3 `supply. The coupling 34 is tubular, as shown, land is provided with an inward tubular extension 35. The coupling 34 is preferably formed of a material similar to the housing 15.` l

Disposed upon the motor shaft 12 a cylindrical adaptor sleeve 36 that-is 'keyed or splined to fthe motor shaft 12 at assembly, by a key 37. The adaptor at one `end has been reduced in diameter'to form a shouldered head portion 38. The impeller 16 comprisesan inner flat circular disc39 and an outer conical disc 40, spaced Vapart a predetermined distance and being of like diameter. The disc 40 hasla relatively large central aperture 41 that receives the extension 35 of the coupling 34 in slightly spaced relation circumferentially. The Vdisc 39 is centrally cylindrically apertu-red at 42 to have seating en- .gagement against lthe shoulder lformed by the reduced portion 38 ofthe adaptor 36. The aperture 42 upon one .side has been notched to receive the key .37, wherebythe impeller and the adaptor will be jointly rotatable under the influence of the shaft 12. The plate 39'is held against the shoulder of the adaptor by a washer 43 that engages the inner side of the plate 39 and with the plate 39 being held against the shoulder and the washer 43 by a screw .44, that has threaded engagement into an axial threaded bore 45 of the shaft 12. A jam washer 46 is preferably Ydisposed between the free end of the shaft 12 and the adaptor. Rigidly connected to the plates '39 and 40 are a plurality of equidistantly spaced and Vradially curved impeller vanes 47. The vanes have their marginal edges Welded to the discs 39 and 40 throughout their'length. As before pointed out, the severalparts have been formed of a similar metal and the impeller discs 39 and 40 and `the vanes 47 are formed of a relatively highly polished :metal free of imperfections that would cause friction or turbulences in the uid being pumped. l

Adapted to be disposed upon the adaptor sleeve 36 to have a yieldable bearing engagement between the irn- Apeller plate 39 and the ring 26, is a tubular compressible seal element, indicated as a Whole by the numeral Y48, vsee particularly FIGURE 8. The seal element 48 is preferably formed of a relatively vtough plastic commonly known in .the trade as Teom The seal element 48 has Ya cylindrical bearing head 49, having a lflat bearing face 49' that has rotative bearing engagement against the ring 26.

The -head 49 has a cylindrical axial bore 50 that is relatively larger in diameter than the diameter of the adaptor 36. The seal element 48 is also axially bored at 50' and with the bore 50 having a diameter for a relatively snug yengagement with the adaptor sleeveV 36. The seal member 48 has been circumferentially grooved forwardly of the head 49 and with the groovesbeing at spaced apart points, as indicated at 51. The inner circumference of the-seal 48 is also circumferentiallv grooved at 52 and with the lgroove 52'being intermediate the space ofthe "grooves'Sl, forming a relatively thin walled compression .section 53 whereby the unit may be Vcompressed in an axial manner to form a constant yieldable seal between ,the .plate 39 and the seal ring 26. The use of Te'on t yas a seal member is known for its inherent qualities, being .toughrin texture, long wearing and that is resistant to acid and the use of the seal element 48 in combination with the ceramic orglass ring 26 constitutes a most desirable seal between the rotative parts. While the ring 26 has Ybeen indicated as being a ceramic, it may be formed of a `sintered carbon or polished glass, each' havinga high lresistance to deterioration under the action of acids.

At assembly, the connector I3 is xedly engaged with the end' of 4the motor by the bolts 19. The seal member .'25 audits supported ceramic ring 26 are then inserted into Athe recessed hub portion 24 and the seal plate 14 installed Ain Vconcentric recessed engagement with :respect to the vconnector. The adaptory sleeve is then engaged over'the shaft 12 and the key 37 inserted within the spline groove of the shaft. The compressible seal member 48 `is then Iengaged over the adaptor' 36, to the point where its 'head Avolume and pressure.

Y peller 16 is then engaged over Ithe hub portion of the adaptor, compressing the seal member 4S to the point Where the plate 39 is fully seated upon the hub portion 38 of the adaptor to rest against the shoulder.` The Washer 43 and the screw 44 are then engaged to clamp the plate V39 against the shoulder of the hub 3S, eifectively clamping the impeller .in rotative engagement with the shaft 12 through the medium of the key 37 and in such assembled relation, the seal element 48 has been substantially compressed and presents a constant pressure between the -p1ate'39 and the ceramic ring 26. The bell housing 15 is then assembled in overlying relation to the tlange 23 and the ring 29 engaged over the several anges and compressed into sealing engagement by the clamping ring 28. The pump thus assembled is ready for installation. The inner end of the adaptor 36 is engaged with a compressibleseal ring 54. The seal ring 54 has a seating engagement against a conical slinger member 55 carried by the shaft 12 whereby to throw any water outwardly that might pass between the seal elements. The band 17 is also provided with a circumferential row of spaced apart apertures 56, constituting drainage and ventilation openings. The bell housing 15 is also provided with a vdischarge pipe 57, that is suitably welded into an opening formed in the housing and with the pipe 57 being tangentially disposed with respect to the housing 15. The pipe 57 lhas a threaded coupling end 58 for coupling engagement with a distribution line.

It will be apparent from the foregoing, that the pump of this invention embodies novel features of construction .and-assembly, all operating to permit the manufacture ythereof in an economical manner and with a major increase in eciency. The manufacture of the pump from polished sheet metal results in a relatively light weight pump that may be sold at .a cost very substantially below the cost of pumps whose parts are cast. The use of polished'sheet metal avoids any rough or uneven surfaces that create uid friction and turbulence, such being generally recognized as a major cause of ineiciency in pump Further, thoroughness of the castings creating turbulence and friction creates an additional load upon the prime mover. The forming of the impeller from polished sheet metal throughout, offers much less resistance to rotation in the fluid to be pumped. The pump, -while being shown as close coupled with the prime mover, it will be clearly apparent that it may be separately mounted and belt driven. A further novel feature of the present invention resides in the extremely simple and eiective clamping and 'sealing means between the several units that comprise the connector, l,the separator and the bell housing, the clamping ring and the seal ring functioning tosimultaneously clamp the sections together vand to seal the ring with respect to the several flanges of the units. Also, the very novel form. of compressible seal means avoids the use of springs or other pressure exerting means to hold the seal elements in frictional engagement. lt will be apparent however that a suitable compression spring may bedisposed Vbetween Ythe impeller and the forward end of the pressure element 48 if desirable although, the use of the bellows type pressure element formed of Teflon has proven highly satisfactory. Thepressure element 48 being formed of plastics offers a very novel yieldable means for sealing the rotatable elements. The use of the ceramic or carbon bearing ring in combination with the plastics seal member 48 also constitutes Va novel arrangementY of seal means that requires no lubrication and that is relatively long lasting and that is resistant to acids and other deteriorating substances. There are no parts Yin the sealing mechanism that may become disarranged or subject to corrosion and rusting.

Basically, the outstanding features of the .pump of this inventionV are as follows:

(1) By making the impeller, and the pump parts of .ancrage polished sheet metal, friction and turbulence within the pump is reduced to lower levels than is possible with castings, even if these are polished, because the degree of polish obtainable within an enclosed impeller or even on curved surface parts is necessarily less perfect than on a at sheet. This means higher efliciency in the pump of this invention.

(2) It is ageneral rule throughout industry that sheet metal parts are of lower cost than equivalent cast parts. This is true in this instance. The pump of this invention is presently being manufactured and sold at a price less than half that of cast pumps made of the same material.

: (3) Where weight is a factor, such -as in planes, etc.,

total weight of the pump is only a small fraction of the conventional cast pumps.

(4) At the present time, titanium, because of its corrosion resistance, strength and light weight, is much sought after as a material for many applications heretofore covered by stainless steel and aluminum. The cost of titanium at present is such that its application to cast pumps makes their price extremely high. Of titanium sheet metal, the price is reduced considerably. This is merely an example of applying the new approach to expensive metals with the inherent weight saving and hence a lower price.

(5) In pumps heretofore employed, where a rotatable seal means is provided between the impeller casing and the separator, it has been customary to employ coil springs or the like to bias the seal elements together and by the use of the novel form of yieldable Teon pressure member, the question of rusting or disarrangement of parts has been avoided.

It is to be understood that the invention is not limited to the precise construction shown, but that changes are contemplated as readily fall within the spirit of the invention as shall be determined by the scope of the subjoined claims.

Having described my invention, what I claim as new and desire to secure by Letters Patent is:

1. A centrifugal pump for close coupled connection with an electric motor having an extended drive shaft, a connector housing for rigidly supporting the pump in engagement with the motor, the pump comprising also a seal plate for the housing and a bell housing, the connector, the seal plate and the bell housing all being circumferentially and concentrically anged, combined sealing and clamping means that engages the several anges whereby to clamp the housing, the seal plate and the bell housing into rigid waterproof engagement, a rotary iiuid impeller disposed in the bell housing concentric thereto, an adaptor that has splined engagement with the shaft of the motor and that has cl-amped engagement with the impeller, a seal device seated within a recess formed in the cover plate axially thereof and concentric to the adaptor, the impeller comprising a pair of spaced apart discs and a plurality of radial vanes that are welded to the discs, a rear disc of the impeller being flat and apertured centrally for fixed engagement with the adaptor, the other plate of the impeller being conical and spaced from the last named disc, an axially disposed tubular inlet connection for the bell housing and a icompressible non-metallic seal device frictionally engaging the adaptor and that bears at one end against the at disc of the impeller and with its opposite end being yieldably held against the iirst named seal element.

2. A centrifugal pump of the character described for operative connection to the end portion of a prime mover, such as an electric motor having a projecting drive shaft, a connector of cylindrical shape having one side iixedly connected to the end of the motor, the opposite side having an outwardly directed circumferential flange, a seal plate for closing the open side of the connector and with the seal plate being formed non-fiat and having a circumferentially arranged outward ange that is concentric to the ange of the connector, the seal platecentrally Y thereof being rearwardly recessed to form a hearing for a compressible seal ring, the seal ring having an inserted non-metallic bearing ring that is concentric to the drive shaft and that projects forwardly of the seal plate, a bell housing for supporting a rotary impeller, the bell housing being closed at its forward side and lprovided with a centrally arranged tubular coupling element, the bell housing :at its opposite side being provided with a circumferential ange that is concentric with respect to the iirst named ange and with the several flanges being in contacting engagement, a compressible seal ring overlying the several anges and a clamping band that overlies the seal ring for compressing the seal ring against the several flanges, the said band also partially overlying the flanges of the connector and the bell housing to force the flanges into contacting engagement, an adaptor sleeve engaging the drive shaft, the sleeve also being splined to the drive shaft, the impeller device including a pairof concentric discs, a rear disc of the impeller being apertured to engagea reduced portion of the adaptor and with the aperture being notched to also receive the spline, a screw device for clamping the disc in splined engagement with the adaptor and with the screw device having threaded engagement into a threaded axial opening of the drive shaft, 'the other disc of the impeller being conical in shape and with the two discs being spaced apart, a plurality of radial vanes iixed to the discs :at their opposite edges and with the conical disc being taxi-ally apertured to partially overlie an inner extension of the coupling device, a pressurizing seal element disposed upon the adaptor in frictional engagement and with a forward end of the pressurizing device bearing lagainst the iiat disc of the impeller, the said pressurizing seal element being formed of plastics and with the pressurizing device at its opposite end having a constant pressurized bearing engagement with the iirst named seal ring, the said bell housing at one side having communication with a discharge pipe.

3. The structure according to claim 2 wherein the ange of the seal plate is slightly less in Adiameter than the flanges of the connector and the bell housing, the said clamping ring -being separable lat one side for engagement over the ange of the connector and the flange of the bell housing, the clamping ring having a clamping screw that compresses the seal ring jointly upon the margins of the several iianges and to simultaneously clamp the several anges together.

4. The structure according to claim 2 wherein the adaptor has -a relatively close engagement with the drive shaft and with the inner end of the adaptor extending through the first named seal device into the connector housing, a slinger flange carried by the drive shaft, a compressible seal ring disposed between the slinger and the inner end of the adaptor, the said connector housing being provided with a circumferential row of spaced apart apertures, the said seal plate being shaped centrally thereof to form a concentric recess for the rst named seal element, the said first named seal device including a compressible ring that is seated into the recess to be substantially flush with the forward side of the seal plate, the said ring adapted to xedly receive a ceramic, glass or carbon bearing ring that is also concentric and in spaced apart relation to the adaptor, the said pressurizing seal comprising Ia plastic cylindrical body that is grooved externally and internally to provide yieldable wall sections in an accordion manner, the said seal device comprising a cylindrical head portion that is adapted to be constantly biased to bearing engagement to the first named bearing ring.

5. The pressurized seal element according to claim 2 that is formed of a molded cylindrical body of tubular form, the body having an enlarged cylindrical head portion that constitutes the seal bearing, the body portion being reduced in diameter toward its opposite end and with the opening of the body portion being relatively Y smaller vthan :the opening dened bythe head portion,

the 'reduced 1opening adapted `to have frictional engagement Vwith the adaptor, 'the reduced body portion being circumferentially grooved at spaced apart points and with the body portion also being additionally internally grooved to form a `pair of yieldable Wall sections that are compressible and that bias the head portion into frictional engagement with the lirst named seal ring and a gasket device disposed between a hub portion of the adaptor and the free end of the drive shaft, the said connector housing, the seal plate, the bell housing, the impeller and the adaptor all being formed of non-corrosive stainless steel. Y

y6. The device'accordingfto claim 4, wherein theY first namedrseal ring'is formedof carbon.

7.. The device according to claim 4, wherein therst named seal n'ng is Vformed of f polished glass.

l8. The deviceaccordingto claim 4, whereinV the rst named seal ring `is formed of ceramic.

References Cited in the iile of .this patent UNITED STATES PATENTS 2,207,371 Blackmore et al. July 9, 194D 2,418,258 Harlamoi Apr. l, 1947 2,745,351 Zozulin May 15, 1956 2,844,100 Heinicke July 22, 1958 

